US5879260A - Toroidal type continuously variable transmission with biasing cam directly connected to a sun gear - Google Patents

Toroidal type continuously variable transmission with biasing cam directly connected to a sun gear Download PDF

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Publication number
US5879260A
US5879260A US08/859,711 US85971197A US5879260A US 5879260 A US5879260 A US 5879260A US 85971197 A US85971197 A US 85971197A US 5879260 A US5879260 A US 5879260A
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United States
Prior art keywords
continuously variable
variable transmission
sun gear
type continuously
toroidal type
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Expired - Lifetime
Application number
US08/859,711
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English (en)
Inventor
Takeo Yoshida
Masaki Nakano
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Nissan Motor Co Ltd
JATCO Ltd
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JATCO Corp
Nissan Motor Co Ltd
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Assigned to NISSAN MOTOR CO., LTD., JATCO CORPORATION reassignment NISSAN MOTOR CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NAKANO, MASAKI, YOSHIDA, TAKEO
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Assigned to JATCO LTD reassignment JATCO LTD CHANGE OF NAME AND ADDRESS Assignors: JATCO TRANSTECHNOLOGY LTD.
Assigned to JATCO TRANSTECHNOLOGY LTD. reassignment JATCO TRANSTECHNOLOGY LTD. MERGER (SEE DOCUMENT FOR DETAILS). Assignors: JATCO CORPORATION
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
    • F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing the toothed gearing having orbital motion

Definitions

  • the present invention relates in general to an automotive transmission, and more particularly to a toroidal type continuously variable transmission which generally comprises a forward/backward switching device with a planetary gear unit, a loading cam device and a toroidal type speed change unit which are coaxially arranged.
  • the planetary gear unit of the switching device is rotatably supported by a fixed annular wall member through a bearing.
  • the bearing In order to suppress excessive rotation speed of the bearing at the time when the planetary gear unit rotates relative to the wall member, the bearing is positioned near a rotation center of the planetary gear unit where the bearing exhibits a smaller peripheral speed.
  • the fixed annular wall member extends radially inward to such a position as to face a pinion carrier of the planetary gear unit.
  • the toroidal type speed change unit comprises input and output cone discs and power (or friction) rollers each being put between the input and output discs to establish a frictional engagement therewith.
  • power (or friction) rollers By continuously changing the inclination angle of the power rollers relative to the input and output discs, speed change is continuously carried out during power transmission from the input disc to the output disc.
  • the loading cam device is employed.
  • the loading cam device comprises a cam disc which is arranged coaxial with the input disc and, cam rollers which are rotatably disposed between respective inclined cam surfaces of the cam disc and the input disc.
  • the cam rollers are held by a holder in a manner to be regulated in relative positioning.
  • the torque applied to the cam disc is transmitted to the cam rollers and then to the input disc.
  • the cam rollers are forced to roll on the respective inclined cam surfaces of the cam disc and the input disc to produce between the cam disc and the input disc a certain thrust in accordance with the transmitted torque. With the thrust thus produced, the power rollers are compressed between the input and output discs.
  • the forward/backward switching device is connected to the loading cam device using the pinion carrier as an output means for the cam disc of the loading cam device.
  • the connection between the pinion carrier and the cam disc has to be made by a separate member which straddles the annular wall member.
  • a toroidal type continuously variable transmission in which, for eliminating the above-mentioned drawbacks, the sun gear of a planetary gear unit of a forward/backward switching device is directly engaged with an input part of a loading cam device.
  • a toroidal type continuously variable transmission which comprises a forward/backward switching device including a planetary gear unit; a loading cam device coaxially arranged behind the switching device to receiving a torque from the planetary gear unit; a speed change unit coaxially arranged behind the loading cam device to receive a torque from the loading cam device; a fixed wall member arranged between the switching device and the loading cam device, the wall member extending to the position of a pinion carrier of the planetary gear unit to rotatably support the planetary gear unit; and a connecting device for directly connecting a sun gear of the planetary gear unit with an input part of said loading cam device to achieve a united rotation therebetween.
  • FIG. 1 is a sectional view of an essential portion of a toroidal type continuously variable transmission which is a first embodiment of the present invention
  • FIG. 2 is an enlarged sectional view of a portion of the transmission of the first embodiment, where a forward/backward switching device and associated parts thereof are arranged;
  • FIG. 3 is a schematic illustration of a forward/backward switching device employed in a second embodiment of the present invention.
  • FIGS. 1 and 2 there is shown a toroidal type continuously variable transmission which is a first embodiment of the present invention.
  • FIG. 1 denoted by numeral 1 is an input shaft and 2 is an output shaft which are aligned in a transmission case 3. As shown, a rear end of the input shaft 1 is received in a bore formed in a front end of the output shaft 2 to effect a relative rotation therebetween.
  • each power roller 6 is compressed between the input and output discs 4 and 5 with a certain biasing force.
  • a cam disc 9 is coaxially arranged in front of the input disc 4, which is mounted on a diametrically enlarged front portion of the output shaft 2 through a ball-thrust bearing 10.
  • the input disc 4 and the cam disc 9 are formed at their mutually facing sides with respective cam surfaces 4a and 9a each being inclined in a radial direction.
  • Cam rollers 11 are rotatably disposed between the cam surfaces 4a and 9a to constitute a loading cam device 12.
  • the cam disc 9 serves as a rotatable input means of the loading cam device 12.
  • the forward/backward switching device 13 which can change the direction of rotation before transmitting the rotation of the input shaft 1 to the cam disc 9 of the loading cam device 12.
  • the forward/backward switching device 13 generally comprises a planetary gear unit 14, a forward clutch 15, a piston member P2 for the forward clutch 15, a backward brake 16 and a piston member P1 for the backward brake 16.
  • the piston member P2 or P1 selectively establishes engagement and disengagement of the forward clutch 15 or the backward brake 16.
  • these piston members P2 and P1 are arranged at front portions of the backward brake 16 and the forward clutch 15, that is, at a remote position from the loading cam device 12 with respect to the planetary gear unit 14.
  • the planetary gear unit 14 is of a single pinion type, which comprises a sun gear 14s.
  • the sun gear 14s is coaxially and rotatably disposed about the input shaft 1 and unitable to the input shaft 1 through the forward clutch 15.
  • a ring gear 14r is connected to the input shaft 1 through a clutch drum 15d of the forward clutch 15.
  • a pinion carrier 14c is connectable to the transmission case 3 through the backward brake 16.
  • a pinion 14p is rotatably supported by a pinion shaft 14f through a pinion is bearing Bp.
  • the planetary gear unit 14 is rotatably supported, through a bearing 100, by an annular wall member 17 which extends radially inward from the transmission casing 3. As shown, the annular wall member 17 is arranged between the forward/backward switching device 13 and the loading cam device 12 and extends to a position to face the pinion carrier 14c.
  • the bearing 100 is positioned at a leading end of the annular wall member 17 where the bearing 100 exhibits a smaller peripheral speed. With this positioning, excessive rotation speed of the bearing 100 can be suppressed.
  • the sun gear 14s is directly engaged or connected with the cam disc 9 of the loading cam device 12. With this, the sun gear 14s serves as a drive means for the loading cam device 12.
  • the sun gear 14s and the cam disc 9 are integrally formed with mutually engaged gears 18 and 19.
  • the gear 18 of the sun gear 14s comprises circularly arranged teeth which are projected toward the cam disc 9
  • the gear 19 of the cam disc 9 comprises circularly arranged teeth which are projected toward the sun gear 14s and operatively engaged with the teeth of the gear 18.
  • Rotation of the input shaft 1 is transmitted to the clutch drum 15d and to the ring gear 14r through the clutch drum 15d.
  • references “O1” and “O2” denote rotation axes of the power rollers 6 and the input and output discs 4 and 5, respectively. It is to be noted that the axis “O1”, extends perpendicular to the surface of FIG. 1.
  • Reference “O3” is a pivot axis about which each power roller 6 pivots.
  • each power roller 6 When the power rollers 6 are shifted in such a manner that the rotation axis "O1" thereof is offset from the rotation axis "O2" of the input and output discs 4 and 5, each power roller 6 is automatically pivoted about the pivot axis "O3" in a direction corresponding to the offset. With this, the positions where each power roller 6 contacts the input and output discs 4 and 5 are changed thereby continuously varying the speed change ratio, that is, the speed ratio between the input and output discs 4 and 5.
  • the gear 18 to which a marked load is applied during direct torque transmission from the sun gear 14s to the loading cam device 12 is integral with the sun gear 14. This means that hardening processing for the gear 14 and the sun gear 14s can be achieved at the same time.
  • the piston members P1 and P2 are arranged at remote positions from the loading cam device 12 with respect to the planetary gear unit 14.
  • operative engagement of the gears 18 and 19 is easily carried out without being obstructed by such piston members P1 and P2. That is, the axial length between the two gears 18 and 19 can be reduced, which brings about a vibration-free torque transmission from the sun gear 14s to the cam disc 9.
  • FIG. 2 is an enlarged sectional view showing an upper half of the forward/backward switching device 13 shown in FIG. 1.
  • This drawing is provided for explaining a unique lubrication oil flowing structure defined in the device 13.
  • the pinion carrier 14c, the pinion 14p, the pinion bearing "Bp" and the pinion shaft 14f are those whose lubrication is not easy.
  • the backward brake 16 is engaged and thus the pinion carrier 14c is fixed, feeding of lubrication oil to the pinion bearing Bp is difficult.
  • the unique oil flowing structure is constructed to effectively lubricate such parts of the planetary gear unit 14.
  • the oil flowing structure comprises a cylindrical portion "S" integrally formed on a front (or left) portion of the sun gear 14s.
  • annular bore “E1” which serves as an oil reservoir.
  • the annular bore “E1” has a diametrically reduced front end which is defined by an annular ridge "X” projected radially inward from the cylindrical "S” of the sun gear 14s.
  • the annular ridge "X” may be provided by caulking the left end of the cylindrical portion "S”.
  • An oil passage “R1" is formed in the sun gear 14s, which extends radially obliquely outward from the annular bore "E1" to a portion exposed to the gear 18.
  • the oil flowing structure further comprises an oil passage "R2" formed in the pinion carrier 14c.
  • the oil passage “R2” has an enlarged inlet part “E2" which faces to an outlet opening of the oil passage "R1" of the sun gear 14s.
  • first and second annular supporting portions 1a and 1b which are axially spaced.
  • the first supporting portion 1a is integral with the input shaft 1, while the second supporting portion 1b is detachably connected to the input shaft 1 through a stop ring.
  • An inner disc part of the sun gear 14s is slidably put between the first and second supporting portions 1a and 1b through thrust bearings "Bs". That is, axial displacement of the sun gear 14s relative to the input shaft 1 is suppressed or at least minimized.
  • any thrust inevitably produced in the forward/backward switching device 13 is effectively absorbed by the input shaft 1 through the sun gear 14s, so that an oil pump housing 20, the loading cam device 12 (see FIG. 1) and the speed change unit "T" are protected from a certain stress caused by such thrust. This brings about a compact and light-weight construction of the transmission.
  • FIG. 3 there is schematically shown a forward/backward switching device employed in a second embodiment of the present invention.
  • the transmission of this second embodiment is substantially the same as that of the above-mentioned first embodiment except the type of the planetary gear unit 14 in the forward/backward switching device. That is, in this second embodiment, the unit 14 is of a double pinion type.
  • the sun gear 14s is rotatably disposed on the input shaft 1 but connectable to the input shaft 1 through the clutch drum 15d upon operation of the forward clutch 15.
  • Two pinions 14p1 and 14p2 are rotatably held by respective pinion shafts 14f1 and 14f2 of a pinion carrier 14c.
  • the pinion carrier 14c is connected to the input shaft 1 through the clutch drum 15d of the forward clutch 15.
  • the support plate 17 rotatably supports both the pinion carrier 14c and the clutch drum 16d.
  • the ring gear 14r secured to an inner wall of the clutch drum 16d is connectable to the transmission case 3 together with the clutch drum 16d upon engagement of the backward brake 16.
  • Rotation of the input shaft 1 is transmitted to the clutch drum 15d and through the same to the pinion carrier 14c which has the two pinions 14p1 and 14p2 rotatably connected thereto.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Friction Gearing (AREA)
  • General Details Of Gearings (AREA)
US08/859,711 1996-05-23 1997-05-21 Toroidal type continuously variable transmission with biasing cam directly connected to a sun gear Expired - Lifetime US5879260A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP8-128249 1996-05-23
JP12824996A JP3447892B2 (ja) 1996-05-23 1996-05-23 摩擦車式無段変速機

Publications (1)

Publication Number Publication Date
US5879260A true US5879260A (en) 1999-03-09

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US08/859,711 Expired - Lifetime US5879260A (en) 1996-05-23 1997-05-21 Toroidal type continuously variable transmission with biasing cam directly connected to a sun gear

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US (1) US5879260A (de)
JP (1) JP3447892B2 (de)
DE (1) DE19721534B4 (de)
GB (1) GB2313424B (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5961415A (en) * 1998-09-17 1999-10-05 Ford Global Technologies, Inc. Single cavity toroidal traction drive continually variable transmission
US6007448A (en) * 1997-08-28 1999-12-28 Honda Giken Kogyo Kabushiki Kaisha Lubrication structure for planetary gear assembly
US20030190993A1 (en) * 2001-02-22 2003-10-09 Exedy Corporation Multiple plate clutch device
US20130130861A1 (en) * 2011-11-23 2013-05-23 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Clutch arrangement for a vehicle drive train
US10927901B2 (en) 2016-07-07 2021-02-23 Unipres Corporation Wet multi-plate clutch
US10927900B2 (en) 2016-03-16 2021-02-23 Unipres Corporation Wet-type multiple plate clutch
US11362566B2 (en) * 2015-03-09 2022-06-14 Kawasaki Jukogyo Kabushiki Kaisha Toroidal continuously variable transmission and integrated drive generator

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3369437B2 (ja) * 1997-04-30 2003-01-20 ジヤトコ株式会社 トロイダル型無段自動変速機の支持壁構造
DE19826096A1 (de) * 1998-06-12 1999-12-16 Zahnradfabrik Friedrichshafen Stufenloses Reibradgetriebe
KR102555350B1 (ko) 2017-08-18 2023-07-12 유니프레스 가부시키가이샤 클러치판 보유 지지용 통상 부품 및 그 프레스 성형 방법

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3410146A (en) * 1966-06-20 1968-11-12 Gen Motors Corp Roller friction transmission
GB1199145A (en) * 1966-09-02 1970-07-15 English Electric Co Ltd Rotary Transmission System
EP0389790A2 (de) * 1989-03-31 1990-10-03 Nissan Motor Co., Ltd. Nockenanpressvorrichtung für ein stufenlos regelbares Toroidal-Getriebe mit Schmiereinrichtung
JPH0539834A (ja) * 1991-08-01 1993-02-19 Nissan Motor Co Ltd トロイダル無段変速機のパワートレーン支持構造
US5478290A (en) * 1994-01-28 1995-12-26 Fairfield Manufacturing Co., Inc. Two speed high shift transmission

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2112763A (en) * 1933-12-28 1938-03-29 Cloudsley John Leslie Variable speed power transmission mechanism
JP2768012B2 (ja) * 1990-12-25 1998-06-25 日産自動車株式会社 無段変速機
JPH04122848U (ja) * 1991-04-23 1992-11-05 日産自動車株式会社 トロイダル型無段変速機
JP3495790B2 (ja) * 1994-07-27 2004-02-09 ジヤトコ株式会社 車両用無段変速装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3410146A (en) * 1966-06-20 1968-11-12 Gen Motors Corp Roller friction transmission
GB1199145A (en) * 1966-09-02 1970-07-15 English Electric Co Ltd Rotary Transmission System
EP0389790A2 (de) * 1989-03-31 1990-10-03 Nissan Motor Co., Ltd. Nockenanpressvorrichtung für ein stufenlos regelbares Toroidal-Getriebe mit Schmiereinrichtung
JPH0539834A (ja) * 1991-08-01 1993-02-19 Nissan Motor Co Ltd トロイダル無段変速機のパワートレーン支持構造
US5478290A (en) * 1994-01-28 1995-12-26 Fairfield Manufacturing Co., Inc. Two speed high shift transmission

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6007448A (en) * 1997-08-28 1999-12-28 Honda Giken Kogyo Kabushiki Kaisha Lubrication structure for planetary gear assembly
US5961415A (en) * 1998-09-17 1999-10-05 Ford Global Technologies, Inc. Single cavity toroidal traction drive continually variable transmission
US20030190993A1 (en) * 2001-02-22 2003-10-09 Exedy Corporation Multiple plate clutch device
US20130130861A1 (en) * 2011-11-23 2013-05-23 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Clutch arrangement for a vehicle drive train
US9005070B2 (en) * 2011-11-23 2015-04-14 Getrag Getriebe-Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Clutch arrangement for a vehicle drive train
US11362566B2 (en) * 2015-03-09 2022-06-14 Kawasaki Jukogyo Kabushiki Kaisha Toroidal continuously variable transmission and integrated drive generator
US10927900B2 (en) 2016-03-16 2021-02-23 Unipres Corporation Wet-type multiple plate clutch
US10927901B2 (en) 2016-07-07 2021-02-23 Unipres Corporation Wet multi-plate clutch

Also Published As

Publication number Publication date
DE19721534A1 (de) 1997-11-27
JPH09310745A (ja) 1997-12-02
GB2313424B (en) 1998-05-13
GB2313424A (en) 1997-11-26
DE19721534B4 (de) 2005-09-01
GB9710739D0 (en) 1997-07-16
JP3447892B2 (ja) 2003-09-16

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